Oscillating piston pump



F. PAULSMEIER ETAL 2,808,006

oscILLATING PIsToN PUMP 2 Sheets-Sheet 1 Oct.y 1,. 1957 Filed nec. 17. 1952 0d. l, 1957 F. PAULsMl-:IER ET AL 2808,006

OSCILLATING PISTON PUMP 2 Sheets-Sheet 2 Filed Dec. 17, 1952 1N VENTORS FR/TZ PALsME/ER vHANS WARSCHAU inf United States Patent ice 2,808,006 Patented Oct. 1, 1957l OSCILLATING PISTON PUMP Fritz Paulsmeier and Hans Warschau, Hamburg, Germany Application December 17, 1952, Serial No. 326,566

2 Claims. (Cl. 10S-117) This invenion relates to an oscillating pistonv pump. It more particularly relates to a new cylindrical oscillating piston pump having a symmetrical inlet anddischarge action.

Rotary universal-joint pumps having a rotary central member with an oscillating displacement piston are well known.

These conventional universal-joint oscillating piston pumps have the marked disadvantage that the liquid being conveyed will exert a unilateralv unsymmetrical force on the rotor and its components. These unsymmetrical forces due to the high pressures per unit area exert extensive wear on the moving parts of the pump and cause high stresses of the rotary shafts and their bearings.

The extremely high valu'es that these stresses reach when the pump is in operation conveying liquids is showny in the following table and indicates average values for pumps of four different sizes:

Av. Size At At 10 At 20 At 50 of the atm. atm. atm'. atm. Delivery in m/hr. area of guage guage guage guage pressure in kg. in kg. in kg. vin kg.

in om.

' These pressures are still further increased by the effect of the suction head formed during the pumping operation. s

One object of this invention is a newcylindrical oscillating piston pump which has a symmetrical inlet and dis-` charge action and therefore will eliminate the stresses caused by the unilateral forces of the liquid being conveyed. This and still further objects will become apparent from the following description read in conjunction with the drawingin which: f

Fig. 1 isa longitudinal section of an embodiment of a pump in accordance withl the invention,

Fig.,2 is a cross-section ofthe-pumpv shownin Fig. 1 in the plane 2`-.-2,

Fig. 3 is a cross-section of the pump shown in Fig. 1 through the plane 3 3,

Fig. 4 is a diagrammatic perspective view of the rotor 3-3a,

Fig. 5 is a diagrammatic perspective view of the piston 2,

Fig. 6 is a diagrammatic view of the housing showing the inlet and discharge passages, and

Fig. 7 is a diagrammatic sectional View taken on the line 7-7 of Fig. 6.

The new pump in accordance with the invention eliminates the stresses which occurred in the prior known pumps by effecting the suction and delivery symmetrically so that the forces produced will completely cancel out each other and the high stresses and wear caused by these stresses will be eliminated.

The symmetrical conveying of a pump in accordance with the invention will additionally eliminate the strong loads of the conveying liquid occurring in the axial direction of the drive shaft and the deection shaft which occurred in the prior known pumps due to the unilateral conveying of the liquids.

The invention will be described in vdetailwith reference to the embodiments'shown in the drawings.

The pump rotor has two symmetrical sides 3 and 3a and rotates on the drive shaft 1 and the shaft 1a axially aligned with the drive shaft. The central portion of the rotor is hollow and is tted with the oscillating piston 2. The piston 2 rotates with the rotor 3-3a and oscillates within the hollow interior of the rotor around the axis of the shaft 8. The symmetrical oscillating pistou positioned for oscillatory motion around the axis yof the shaft 8 within the symmetrical hollow interior of the rotor 2 forms four chambers 5, 5a, 6 and 6a. The chambers 5 and 5a are diagonally opposed to each other and symmetrically positioned in relation to each other on opposite sides of the axis of rotation of the rotor. The chambers 6 and 6a are also symmetrical in relation to each other and diagonally oppose on `opposite sides of the axis of rotation of the rotor. j

' A guide ring 4 is positioned circumferentially around the oscillating piston 2. The plane of the guide ring 4 is inclined to the plane of rotation of the rotor as shown by the dotted lines in Fig. 1. The ring 4, as shown in Fig. 2, will, therefore, either assume the position 4a or 4b. The ends of the oscillating piston 2 are guided in the guide ring 4 by means of the studs 9 and 9a which ride in the ring 4. Due to the inclined position of the guide ring 4in relation to the plane of rotation of the rotor, the oscillating piston 2 is caused to oscillate back and forth as the shaft 1 and the rotor 3-3a rotate.

If the tilting of the guide ring 4 is made adjustable by means of the shaft 10 and bearing 11, then the degree of pumping action and the direction of pumping may be controlled by mere adjustment of the degree of tilting of the ring. As shown in Fig. 2 the guide ring 4 is tiltable between a position 4a and 4b. In the position 4a, the pump will pump in one direction to the maximum amount and in the position 4b, the pump will ypump in the opposite direction to the maximum amount. The tiltingof the guide ring 4 thus adjusts the amount that the oscillating piston 2 oscillates and theV direction in which the oscillation is eifected in relation to the rotation ofthe drive suction side 12 and kthe vliquid outlet from ythe' pump on` the discharge side 13. The housing also defines the suction and discharge passages in communication with the chambers 5a and 6a in the hollow interior of the rotor.

In operation, the drive shaft 1 is rotated with the guide ring 4 positioned in the desired tilted position. The rotor S-Sa will rotate rotating the oscillating piston 2 therewith. The ends of the oscillating piston 2 carry the studs 9-9a which are guided in the guide ring and travel around in the guide ring. As the rotor 3-3a and the piston 2 thus rotate, the traveling of the studs 9 in the guide ring will cause the piston to oscillate back and forth within the hollow interior of the rotor causing pumping action in the conventional manner.

On the suction side of the pump as the piston oscillates liquid will be drawn into the chamber 6 and at the same time into the diametrically opposed chambera as shown by the arrows in Fig. 1. At the discharge side of the pump, liquid will be forced out of the chamber 5 and at the same time out of the diametrically opposed chamber 5a in the direction of the arrows. `Thus all the forces of the liquid caused by the pumping will counteract each other and no undesirable and Awear causing stresses will be formed as was the case in the prior known pumps.

It can be plainly seen from Fig. l that thus a portion of the delivery chamber lies about the plane C-D while an equal portion lies below the same plane. The same istrue with the inlet chamber with equal portions lying on each side of the plane CD. The corresponding portions of the inlet 'and delverychambers are `also diametrically opposed to each other. Thus 'for each suction or discharge action of one of these parts of the suction ordischarge chambers respectively, there is a precisely diametrically opposed action of the other part. This, of course, will cause all the individualforces tocancel each other. In this manner, the injurious effects of the former unilateral loads in the known universal-joint pumps are eliminated and the new pump maybe built without difculty for the highest pressures and with the largest dimensions.

T he pump may be used for the conveying of any uids including` liquids and gases. If it is desired that the `pump be used `as a prime mover, it is only necessary to force a tiuid therethrough and utilize the rotation of the drive shaft 1 asdesired. b

Though the invention has `been described with reference to a speciiic embodiment, :many modifications and variationswill become apparent to the skilled artisan within the spiritv thereof.

Thus, the cylindrical oscillating piston pump of the applicant essentially comprises a pump housing with a rotor mounted for rotation in the housing. The rotor defxnes'in the interior thereof afpiston chamber. This piston chamber has substantially symmetrical opposed portions on opposite sides of the axis of rotation of the rotor. An oscillatory piston is positioned in the chamber, defined lin the interior of the rotor. The piston rotates with the rotor and oscillates on an axis which is transverse to the axis of rotation of the rotor and passes through the axis of rotation. The piston has opposed substantiallyv symmetrical members on opposite sides of its axis of oscillation. One of these members is positioned in` each of the opposed symmetrical portions of the piston. The piston thus defines in the chamber sym-V chamber. metrical pairs of suction and discharge chambers. Each member of each pair of chambers is positioned on Vda@ metrically opposite sides of the axis of rotationof the rotor. A stationary guide ring is circumferentially positioned about the piston in a plane tilted to the plajne,

of rotation of the rotor in guiding engagement with at least one end of the piston forcausing oscillation of the pistonuas the rotor rotates. The pump housing defines fluid inlet and uid outlet passages` in communication with the suctionand discharge chambers defined within the rotor. The rotor .of the pump. is connected to a drive shaft for rotation therewith.

Fig. 4 shows the cylindrical rotor 3,-3a with the oscillating piston 2 with the engaged guide ring. The suction .chambers 5a and 6 are shown dark. Whilst the contents of chamber 5a are discharged the chamber 6 is filled. This applies as well for the chambers 5 and 6a positioned on the opposite side, which are not seen in the perspective.

The shafts 1 and 1a show in this sketch that the rotor 3-3a is supported on two sides. By this method not only high one sided loads are avoided but also each one sided thrust due to couples of forces.

Fig. 5 shows the oscillating piston 2 with the shaft 8 and the engaging bore 9.

Fig. 6 shows a circulation of the liquid conveyable from the flow ange 12 or the chamber 6 respectively to the chamber 6a positioned on a diametrically opposite side or from the ow ange 13 or the chamber 5 respectively to the chamber 5a positioned on a diametrically opposite side or vice versa, if the ring 4 is guided e. g. from 4a to 4b over zero-point at the same turning direction of the driving engine.

Outside of the housing 7 is the connectingor circulating-channel guiding around the tightening zone 14.`

Fig. 6 shows the channel as per the Section line g-t of Fig. 7.

We claim:

`1. Cylindrical oscillating piston pump comprising a pump housing, a rotor Arotationally mounted within said housing, said rotor defining in the interior thereof a piston chamber having substantially symmetrical opposed portions onopposite sides of the axis of rotation of the rotor, an oscillatory `piston positioned in said chamber for rotation with said rotor and oscillation about an axis substantially transverse to said axis of rotation and passing therethrough, said piston having opposed substantially symmetrical members positioned in said opposed portions of the piston chamber to define in said chamber substantially symmetrical pairs of suction and discharge chambers, each chamber of each pair being positioned on a diametrically opposite side of said axis of rotation to the other chamber, a stationary guide `ring circumferentially positioned about said piston in a plane tilted to the plane of rotation of the rotor in guiding engagement with at least one end ofrrsaid piston, said guide ring being adjustably positioned in said housing for adjusting the angle of tilt thereof in relation to the plane of rotation of said rotor, said housing defining inlet and discharge passages in communication with said `suction and discharge chambers, and a drive shaft'connected for rotation with said rotor.

2. Pump according to claim l in which the ends of said opposed members of said piston are positioned in guiding engagement with said guide ring.

References Cited in the tile of this patent UNITED STATES PATENTS 826,985 Appel July 24, 1906 1,967,167 Weis July 17, 1934 2,353,780H yNeuland July 1S, 1944 2,380,886 Waldie July 31, 1945 2,431,122 Jakobsen Nov. 18, 1947 2,584,426 Crane Feb. 5, 1952 

